Control system



March 1940! w. 5. DUfiRINGER 2,193,192 CONTROL SYSTEM madam. "4. 1956 2 Sheets-Sheet 2 1| llll I! l l h 1/1/4475? I. p/[E/NGER Patented Mar. 12, 1940 UNITED STATES PATENT OFFICE CONTROL SYSTEM Walter E. Dueringer, Shaker Heights, Ohio, assignoi' to Bailey Meter Company, a corporation of Delaware Application January 4, 1936, Serial No. 57,544 Y 26 Claims.

This invention relates to control systems for regulating the rate of application of an agent or agents contributing to the production of a variable to maintain the variable at a predetermined value. More particularly my invention relates to V One object of my invention is to provide a control system wherein an arbitrary high. speed repositioning of the regulators for the various 15 agents is eifected upon a change in the rate of operation of the devices supplying the agents.

A further object of my invention is to provide a control system instantly correcting for changes in the rate of operation of an agent supplying 2o device, which changes would otherwise produce an alteration in the rate of agent supply beyond that necessary to maintain the variable at the desired value.

A further object of my invention is to provide 25 a control system wherein throughout the duration of transient conditions which produce a marked change in the availability of the agents contributing to the production of a controlled condition a correction is automatically made 30 whereby the rate of supply remains normal at the desired amount.

Still another object of my invention is to provide a control system embodying certain safety features to prevent the establishment of danger- 35 ous or hazardous conditions.

'A further object of my invention is to provide a control system wherein abnormal transient conditions effect a modification of the normal control for their duration.

0 A further object of my invention is to provide a control system wherein an abnormal change in the rate of supply of one agent immediately effects a corresponding change in the rate of supply of another agent, so that the desired in- 4,5 ter'-relation between the agents is continuously maintained.

A more specific object of my invention is to provide a control system wherein upon a change in fan speed, which for example forms a part 50 of the air supply means of a vapor generator, the

damper regulating the air supply is immediately positioned so that the rate of air supply during and after'the change in speed is substantially the same as before the change. I

55 Further objects will be apparent from the follongitudinal lowing description and from the .drawings in which: i

Fig. 1 is a diagrammatic illustration of my invention applied to the control of a vapor generator.

Fig. 2 is a modification of my invention as illustrated in Fig. 1. i

Fig. 3 illustrates another modified form of my invention over that illustrated in Fig. 1.

Fig. 4 illustrates a further modified form of my invention over that illustrated in Fig. 1.

Figs. 5 and 6 are modifications of my invention in connection with hydraulic couplings.

Figs. 7 and 8 illustrate substitute forms of switches which may be used with my control system.

Referring to Fig. 1 I have therein shown my invention applied to the control of a vapor generator I having a combustion chamber 2 to which the elements of combustion comprising fuel and air are admitted through a burner 3 and port 4. respectively. The gaseous products of combustion are withdrawn through an uptake or stack 5 by means of a fluid impeller such as a fan 6 driven by a multi speed motor 7. Generated vapor passes through a conduit 8 to any desired point of usage (not shown). The rate of fuel supply may be regulated by means of a valve 9 positioned in a fuel supply pipe l0; and the rate of air supply may be regulated by means of a damper, positioned in the uptake 5. The rate of air supply may be further regulated by varying the speed of the fan 6.

The regulating valve 9 is adapted to be positioned by a diaphragm motor l2 sensitive to fluid pressures established by a pilot valve I3 and transmitted through a pipe Hi. The pilot valve I3 is preferably of the type disclosed and claimed in the patent to Clarence Johnson, No. 2,054,464 granted September 15, .1936, and has a cylindrical passageway through which a constant flow of pressure fluid from any suitable source (not shown) is maintained from a centrally located inlet port IE to waste outlets at either end. A movable valve stem I6, cen- 5 trally located in the passageway, has mounted thereon a pair of spaced suitably shaped valve members having a maximum diameter slightly less than that of the passageway; and each located substantiallyadjacent to a relatively nar- 0 row annular outlet port connected to the exterior of the valve by a suitable passageway. The pressure fluid in passing the valve members establishes a pressure gradient; and the pressure established at the adjacent outlet port depends application to Clarence Johnson, Serial upon the axial position of the valve member. In the mid or neutral position of the valve stem IS the pressure at both. outlet ports is equal, upward movement of the valve stem producing proportionate increases in pressure at the upper outlet port, and proportionate decreases in pressure at the lower outlet port. Accordingly a loading pressure may be obtained varying directly with the variable to be controlled or inversely thereto depending upon whether the loading pressure established at the upper or lower outlet port is used. The loading pressure so established may be utilized directly as, for example, in Fig. 1 where the loading pressure is transmitted directly from pilot l3 through pipe I4 to the diaphragm motor l2; or it may be utilized to indirectly control the operation of' such devices as hereinafter illustrated. With the arrangement shown in Fig. 1 as I desire the loading pressure to vary inversely with vapor pressure, that is, for a given increase in vapor pressure to produce a proportionate decrease in loading pressure, connection is made to the lower outlet port. In practice a. suitable plug or' stopper may be inserted in the outlet port not in use, or as desired in some cases, connection may be made to both the upper and lower outlet ports.

The valve stem I6 is pivotally connected to a Bourdon tube |1 sensitive to variations in vapor pressure within the conduit 8, by a link I8 and beam l9. As the pressure of the vapor decreases, the valve stem I6 will be positioned downwardly as viewed in the drawings, increasing the loading pressure within the pipe I 4 and positioning the valve 9 in an opening direction; conversely, as the pressure of the vapor increases, the valve stem l6 will be positioned upwardly effecting a positioning of the valve 9 in a closing direction.

The damper H is positioned by a fluid pressure servomotor generally indicated at 20, and. of a type forming part of the subject matter'of an No. 658,376, filed in the United States Patent Oflice February 24, 1933, now Patent No. 2,074,696. The damper II is linked by a connecting rod 2| to a piston 22 movable in a cylinder 23. Fluid pressure is admitted to the cylinder 23 at opposite sides of the piston 22 through pipes 24 and 25 connected to the upper and lower outlet ports of a pilot |3A similar to pilot valve vl3. Accordingly, asthe stem |6A moves upwardly from the neutral position, pressure within the pipe 24 increases, whereas that within the pipe 25 decreases, positioning the piston 22 downwardly. Similarly, upon the stem 6A being positioned downwardly from the neutral position, the pressure within the vpipe 25 increases, whereas that within the pipe 24 decreases, positioning the piston 22 upwardly.

The valve stem |6A is positioned by a suitable pressure sensitive bellows 26 mounted on a projection of the cylinder 23 and sensitive to pressures within a pipe 21. In order that the damper by the spring 26 act upwardly. Upon movement ,Of the valve stem |6A downwardly from the neudirection. Upward movement of the connecting rod 2| will progressively increase the upwardly acting force of the spring 29 upon the bellows 26, which will, when the movement of the piston 22 is in proportion to the change in pressure within the bellows 26 restore the valve stem I6A to the neutral position. It is evident therefore that for each magnitude of pressure within the bellows 26 there will be a corresponding definite position of the piston 22 and damper II.

As preferably the rate of air supply is varied in parallel with the rate of fuel supply, I pro vide means for producing pressure variations in the pipe 21 proportional to pressure variations in the pipe J4. To this end I show a Bourdon tube 3| sensitive to pressures within the pipe I4, and pivotally connected to a valve stem |6B of a pilot valve |3B through a link 32 and beam 33. The loading pressure available at the upper outletport of the pilot valve I3B, which is directly proportional to the pressure within the pipe I4, is transmitted through a pipe 34 to a chamber 35 of an averaging relay 36.

Loading pressures effective through pipe 34 upon chamber 35 are balanced against pressures established in a relay chamber 31, to which the pipe 21 is connected, through the agency of opposed diaphragms 38 and 39, operatively connected by a movable member 40. Admission and discharge of pressure fluid from the chamber 31 is controlled by a pivotally supported, horizontal valve member 4| operating a fluid supply valve 42, connected to a suitable source (not shown), and an exhaust valve 43. The arrangement is such that upon an increase in loading pressure within the chamber 35 the member 40 moves downwardly, opening the fluid pressure supply valve 42 until the pressure within the chamber 31 is equal to, or in desired proportion to, that established in the chamber 35, when the member .40 is restored to the neutral position. The initial pressure relation at which the member 40 is in the neutral position may be varied as desired through the agency of an adjustable spring 44. Pressures within the pipe 21 will bear a definite relation to loading pressures established by the pilot 13B, and accordingly, the damper II will be positioned in direct proportion to changes in vapor pressure, and in parallel with the fuel supply valve 9.

As known, for optimum combustion efliciency fuel and air must be supplied in predetermined fixed ratio. To supply air in excess of that required creates a loss due to heating such excess to the temperature of the flue gases. Conversely to supply less air than that required results in incomplete combustion of the fuel. While the combustion control which I have so far described varies the fuel and air together, or in parallel,

there is no assurance that the predetermined ratio resulting in optimum combustion efliciency will be maintained throughout the range of operation, due for example to divergence of damper characteristics as compared to valve characteristics. Accordingly, notwithstanding that the rate of air flow may be correlated to the rate of fuel flow at some particular rate of flow of the latter, such ratio may not be maintained at other rates. To assure that air is continuously supplied in correct ratio to the rate of fuel supply, I show in Fig. 1 means for modifying the rate of air supply to, maintain the desired ratio.

To maintain a predetermined ratio between the 1,257,965 to Bailey. Such a relation gage may be used to determine the ratio between the rate of flow of products of combustion, which as known is an indication of the rate of air supply to the generator; and the rate of flow of vapor which as likewise known is a measure of the rate of fuel supply. I show in Fig. 1 a meter diagrammatically indicated at 850f the rate of vapor flow through the conduit 8 provided with an indicator 46 adapted to move upwardly upon an increase in the rate of flow of vapor from the generator. A similar meter 4'! provided with an indicator 48 measures the rate of flow of the products of combustion through the vapor generator l. The indicator 48 is adapted to move downwardly as the rate of flow of products of combustion increases.

Depending from the indicators 56 and 48 are links 49 and 50 respectively, pivotally supporting a horizontal link 5|. So long as the desired ratio is maintained the mid-point of the horizontal link 5| remains stationary. When, however, the actual ratio of vapor flow to air flow is less than the desired ratio the mid-point of the horizontal link 5| will be lowered proportionately. Conversely when the actual ratio is greater than the desired, the mid-point will be elevated proportionately.

To produce a fluid pressure varying in accordance with deviations of the actual from the desired ratio I show the mid-point of the horizontal link 5| pivotally connected to a valve stem I60 of a pilot valve I30. The pilot valve I30 is similar to the pilot valve l3 and establishes a loading pressure in an outlet pipe 52 proportional to the ratio between rate of vapor outflow and air flow. As the ratio increases the loading pressure within the pipe 52 decreases, and as the ratio decreases the loading pressure will increase.

The pipe 52 connects to a chamber 53 of the averaging relay 36 through a throttling valve 54 having a movable or adjustable stem 55. Pressures within the chamber 53 serve to modify the pressures within the chamber 35 so that control pressures established within the chamber 31 vary remains as desired no further change in the rate of air supply will occur. However, if the increase in rate of air flow instigated by the increase in loading pressure within the chamber 35 produces a greater change than that required to maintain the correct ratio the pilot stem I50 will be displaced downwardly effecting a decrease in pressure within the chamber 53, thereby serving to decrease the rate of air supply.

The throttling valve 54 serves to delay the effectiveness of a change in loading pressure produced by a variationin vapor flow-air flow ratio until the change in fuel flow has been efiected. Obviously while a change in position of the damper II will immediately effect the rate of air supply, a change in fuel flow will not instantly effect a change in the rate of vapor outflow, due to the heat capacity of the vapor generator I, time required for combustion, etc. Accordingly if the throttling valve 54 was eliminated, a change in the existing position of both the valve 9 and damper I I dictated by a change in vapor pressure would immediately act to produce the required change in rate of air supply, which would cause a positioning of the indicator 48, producing .a

change in pressure within the chamber 53, which would serve to nullify the effect of the change in pressure within the chamber 35 produced by the change in vapor pressure and serve to position the damper H to the original position. As the valve 9 had originally been positioned in parallel with the damper l l a deficiency or greater excess of air than required would result, due to the nullifying action of the change in pressure within the chamber 53. The throttling valve 54 therefore serves to delay the action'of the ratio sensitive pilot l3C until changes in fuel supply have been reflected in changes in vapor outflow. In general, therefore, the control system shown in Fig. l'acts to immediately vary both fuel and.

air in parallel upon a change in vapor pressure and thereafter to readjust the rate of air flow to maintain a desired ratio between rate of vapor outflow and rate of air flow. It is, of course, apparent that certain modifications may be made in the method of control while still employing the same basic principles. Thus, for example, if the combustion chamber 2 was provided with solid fuel, on a grate, or in other form, it might then be advisable to vary the rate of air supply in accordance with variations in vapor pressure and readjust the rate of fuel supply in accordance with the ratio between vapor outflow and air supply. The methods of control which I have described are however well known in the art and comprise no part of my present invention.

When the damper H is positioned to a substantially wide open position, indicating that the maximum rate of air supply has been reached for the then existing speed of the fan 5, an arm 56 secured to the connecting rod 2| is arranged to close the normally open mercury switch 5i. Closure of the switch 51 efiects energization of the solenoid relay generally indicated at 58 by a suitable source 59. So long as the switch 57 is open, the motor l is connected to the source 59 through a suitable resistance 68 and a relay finger 6i. Energization of the solenoid switch 58 acts to cut out the resistance 60 and connect the motor 7 directly to the source 59 through a finger 62 thereby increasing its speed.

To prevent the motor I from reverting to the original speed as soon as the damper II is positioned to a partially closed position, energization of the solenoid 58 by closure of the mercury switch 5'l is arranged to immediately provide permanent energization through a normally closed mercury switch 63 and relay finger 64. Notwithstanding,-therefore, that the damper ll maybe moved to a partially closed position opening switch 51, the solenoid 58 will remain energized, thereby maintaining the motor 1 at high speed. Whenthe damper H is positioned to a nearly closed position the arm 56 is arranged to open the switch 63, thereby deenergizing the solenoid 58 and reducing the speed of the motor I by again introducing the resistance 60 into the circult.

caused by the change in' fan speed. The desired operation being for example, that upon an increase in the rate of vapor outflow through the conduit 8 the damper II will be positioned in an' Operation of the switches 51 and 63 produces opening direction until susbtantially wide open, when the switch 51 vwill close increasing the speed of the fan 6. During the period of transition when thefan 6 is increasing in speed the damper II should be positioned proportionately in a closing direction so that the rate of :fiow of.

the products of combustion through the uptake 5, and accordingly the rate of air supply to the combustion chamber 2, will remain substantialy constant. The control system which I have thus far described will function to eventually counteract the change in fan speed through the agency of the ratio sensitive pilot I3C, which operates to maintain the desired ratio between the rate of vapor outflow and rate of air supply. However, due to the delayed action produced by the throttling valve 54 for a period of time following the change the rate of air supply will be far in excess, or greatly less, than that required to effect proper combustion for the then existing rate of fuel supply. Such sudden changes in the rate of air supply may also be of sufficient magnitude to snuff out the flame within the combustion chamber, thereby creating a dangerous and hazardous condition.

I provide for positioning of the damper II in consonance with changes in speed of the fan 6 whereby the rate of flow of the products of comb'ustion through the uptake 5 remains substantially constant during the period of transition from one fan speed to another. To this: end I show pivotally connected to one end of the beam 33 a plunger 65 of a solenoid 66. With the fan motor I energized through the resistance 60, the solenoid 66 is deenergized. Upon the solenoid 58 being energized, however, the solenid 66 is connected to the source 59 through the finger 62, moving the plunger 65 downward a predetermined amount depending upon the axial adjustment of nut 61. Downward movement of the plunger 65 produces a similar movement of the pilot stem I6B effecting a decrease of the loading pressure within pipe 34 which is immediately effective through the relay 36 to position the damper II in a closing direction. By proper adjustment of the nut 61 the change in loading pressure effected within the pipe 34 may be made 'suflicient to substantially counteract or annul the change in rate of flow of the products of combustion through the uptake 5 due to the change in speed of the fan 6.

If now the pressure of the vapor within the conduit 8 should increase, the damper ll would be positioned further in a closing direction until at some predetermined point the arm 56 opened the mercury switch 63, deenergizing the solenoid 58. Such deenergization would disconnect the solenoid 66 from the source 59 and the plunger 65 would move upwardly, increasingthe loading pressure within the pipe 34, which through relay 36 would effect a positioning of the damper II in an opening direction suflicient to counteract the decrease in the rate of flow of products of combustion through the uptake 5 caused by the decrease in speed of the fan 6. The rate of change in the rate of fiow of the products of combustion caused by the positioning of the damper III may be made substantially equal to that effected by the acceleration or deceleration of the fan 6 by proper adjustment of a throttling valve 68 interposed in the pipe 34. The throttling valve 68 serves to vary the rate of positioning of the damper II so that during the period of transition 'from one fan speed to another the rate of fiow of the products of combustion, and accordingly the rate of air supply to the furnace, remains substantially constant.

In the event of failure of the fan 6 or motor I resulting in the stoppage of the flow of products of combustion through the uptake 5 it is desirable that the flow of fuel to the furnace be immediately cut off to prevent the establishment of an explosive mixture therein. To provide for the stoppageof fuel flow in the event of fan or motor failure I show a solenoid generally indicated at 69 connected in the electrical circuit which includes the motor I. Normally the solenoid 69 is energized and finger I is open. Upon failure of the fan 6 or motor I the solenoid 69 will be deenergized due to the opening of the usual circuit breakers, thermal cut-outs, or other protective means (not shown) connected in the circuit of the motor I. Such deenergization will result in closure of thefinger III, which will permit energization of a solenoid II having a movable plunger I2 pivotally connected to one end of the beam I9. Energization of the solenoid II will effect upward positioning of the valve stem I6 in an amount suiiicient to decrease the loading pressure established in the pipe I4 to position the valve 6 to a tight closed position, thereby completely stopping the flow of fuel to the furnace. Simultaneouslythe valve stem I6B will be positioned downwardly, decreasing the pressure within the pipe 34 a suflicient amount to position the damper I I to a minimum position. Reenergization of the electrical circuit of the motor I will result in the solenoid 69 opening the finger IILand permitting the control system to function in normal manner.

In Fig. 2 I show a modified form of my invention adapted to effect proper repositioning of the damper II when the speed of the motor I is controlled by a drum controller such as indicated at I3. As known a drum controller may be provided with a desired number of resistances, circuit modifying devices, etc. (not shown) whereby the speed of a motor may be progressively varied through any desired number of steps.

In Fig. 2 the connecting rod 2| .is arranged to momentarily close normally open mercury switches I4 and I at extreme positions of the damper I I. The switches I4 and are arranged to control the starting of a reversible pilot motor I6 operatively connected to the drum controller I3 through suitable gearing. The pilot motor I6 may be provided with suitable running switches as known so that upon being energized through the momentary closure of switch I4 or I5 operation will continue until the drum controller advances one notch, whereupon further operation will cease until there is a further-momentary closure of switch I4 or I5. Upon closure of the switch H the reversible motor 16 will be operated in a direction to increase the speed of the motor I, whereas upon closure of the switch I5 the reversible motor I6 will be operated to decrease the speed of the motor I.

To provide for the repositioning of the damper II upon a change in speed of the motor I I have provided means for progressively modifying the loading pressure established by the pilot I3B in accordance with the speed of the motor I. Adapted to be energized by the switch I4 is a solenoid II of the double acting solenoid switch generally indicated at I8, The opposite solenoid I9 is adapted to be energized by closure of the switch I5. Energization of the solenoid II closes the finger 60, thereby connecting a field 8| of a reversible motor 62 to the source 59. Conversely energization of the solenoid l9 affects closure of the finger 83, energizing opposed field 84, causing rotation of the motor 82 in opposite direction.

Rotation of the motor 82 through energization of the field 8| effects clockwise positioning of the beam 33 through the agency of a suitable cam 85 operatively connected to the rotor of the motor 82 through suitable reduction gearing. Energization of the field 84 eifects counterclockwise positioning of the beam 33. Such positioning of the beam 33 is effective for progressively modifying the pressure within the pipe 34.

In order that the loading pressure within the pipe 34 will be modified sufiiciently to position the damper II to substantially counteract the change in rate of flow of the products of combustion through the uptake 5 caused by a change in speed of the motor 1, the relay 18 may be provided with a finger 89 which upon energization of the solenoid 11 will sustain energization notwithstanding the fact that the switch 14 may be opened due to the repositioning of the damper II. A similar sustaining finger 81 is provided for the solenoid 19. The solenoids 11 and 19 are connected to one side of the source 59 through a common conductor 88 in which is connected a snap switch diagrammatically indicated at 89, and provided with a movable member 90 operatively connected to the motor 82.

In operation, upon the damper ll being positioned to a nearly wide open position the switch 14 will close, starting operation of the pilot motor 16 which will continue until the drum controller 13 has advanced one notch, increasing the speed of the motor I. Simultaneously the solenoid 11 will be energized, effecting through finger 86 energization of the field8l. Rotation of the motor 82 will then occur in a direction to position the pilot valve stem IGB downwardly, effecting a decrease in loading pressure within the pipe 34, immediately effecting a positioning of the damper H in a closing direction. Opening of the switch 14 will not effect deenergization of the solenoid 11, however, due to the sustaining finger which provides for the energization of the solenoid 11 from the source 59. Rotation of the motor 82 will also eventually throw the movable member 90 of the snap switch 89, thereby effecting deenergization of the solenoid I1 and field 8|. By proper shaping of the cam the downward positioning of the valve stem IGB can be made just sufficient to substantially counteract or annul the increase in rate of flow of the products of combustion through the uptake 5 due to the increase in speed of the fan I.

If clue to a further decrease in vapor pressure within the conduit 8 the damper II is again positioned to a nearly wide open position, the switch 14 will again be energized and the above procedure repeated. Upon a positioning of the damper I l to a nearly closed position the switch 15 is closed, which is effective for starting the motor 18 in opposite direction and which will continue to operate until the drum controller 13 has been retarded one notch. Simultaneously the solenoid 19 will be energized eflecting through the finger 83 energization of the field 84, causing an upward positioning of the pilot valve stem I6B. Such upward positioning will efiect an increase in loading pressure within the pipe 34, thereby positioning the damper H inan opening direction sufficient to counteract the decrease in rate of flow of the products of com-' bustion caused by the decrease in speed of the motor 1. Upon the loading pressure within the nine 34 having changed a predetermined amount, the movable member will operate to deenergize the solenoid 19, thereby deenergizing the field s4.

In Fig. 3 I disclose a further modified form of my invention over that illustrated in Fig. 2. Herein the normally open switches" and 15 are adapted to momentarily energize solenoids 9| and 92 respectively upon closure. The solenoid 9| is pivotally connected to the beam 33 and upon energization an associated plunger 93 will be positioned downwardly, eifecting a similar positioning of the pilot valve stem [63, thereby decreasing the loading pressure within the pipe 34 and efiecting a positioning of the damper II in a closing direction. Upon the 'damper I l moving in a closing direction the switch 14 will be opened, deenergizing the solenoid 9|. The plunger 93 will not however immediately return to the deenergized position to which it is urged through the action of springs 94 and 95, but such action will be delayed due to the retarding effect of The arrangement dashpot arrangement 95. serves, therefore, to position the damper II in a closing direction upon anincrease in speed of the fan 6 and thereafter to gradually remove the.

effect causing such closure, allowing the damper H to again come under the normal control sensitive to variations in pressure within the conduit 8 and variations in the ratio between the rate of vapor outflow and rate of air supply. By proper adjustment of the dashpot 98 the rate at which the loading pressure within the pipe 34 is perinitted to retum to normal may be made equal to the rate at which variations in the rate of air supply affect the pressure within the chamber 53 of the relay 36. Upon an increase in fan speed.

therefore, and a repositioning of the damper II to a partially closed position under the influence of the solenoid 9|, no further positioning of the damper II will occur except as indicated as necessary through further variations in vapor pressure, as increases in pressure within the pipe 34 and chamber 35 of the average relay 36 due to the gradual restoration of the plunger 93 to the deenergized position will be counterbalanced by corresponding decreases in pressure within the chamber 53 upon the ratio of vapor flow to air flow tending to depart from that desired.

Closure of the switch 15 efiects opposite action through energization of the solenoid 92, which effects an increase in pressure within the pipe 34, causing the damper II to be positioned in an opening direction. Upon opening of the switch I5 the solenoid 92 is deenergized and the beam 33 gradually permitted to return to the normal position under the Influence of springs 94 and 95.

In Fig. 4 I show a further modified form of my invention wherein I automatically remove the throttling action of the valve 54 during fan speed changes, so that as the rate of flow of the products of combustion changes, as a result thereof, animmediate proportionate change in the loading pressure within the chamber 53 occurs and serves to position the damper H in a direction to prevent such changes. The Bourdon tube 3| is shown directly connected to the pilot for positioning the damper I I. Upon the damper II being positioned to an open or closed position the switch 14 or 15, respectively, is closed, producing operation of a reversing pilot motor 91, provided with suitable running switches (not shown), in proper direction to produce a desired increase or decrease in speed of the fan 6. To efiect this end the pilot motor 91 is shown operatively connected to a movable arm 98 of a rheostat 99 connected in the circuit of the motor 1. Closure of the switch 14 may for example serve through the pilot motor 91 to reduce the effective resistance connected in circuit with the motor 1. Likewise closure of the switch 15 may serve to increase the effective. resistance connected in circuit with the motor 1.

Connected in parallel with the circuits of the pilot motor 91 and adapted to be energized by either the switch 14 or 15 is a solenoid I00 having a plunger IOI connected to the movable stem 55 of the throttling valve 54. Upon'closure of either the switch 14 or 15 the solenoid I00 is energized, moving the stem 55 to the right as viewed in the drawings, thereby removing the throttling action of the valve 54. Loading pressures produced by the pilot I3C are thereby immediately efiective within the chamber 53 and immediately eifect a positioning of the damper II. Accordingly as the speed of the fan 0 is accelerated, or decelerated, destroying the correct ratio between rate of vapor outflow and rate of air supply, the loading pressure produced by the pilot I3C is proportionately varied, but in a direction positioning the damper II to change the rate of flow of the products ofcombustion in opposite sense to that caused by the change in speed of the fan 6. Such positioningof the damper II will continue until the correct ratio between vapor flow and air flow is reestablished.

Upon the damper II being positioned in response to variations in the loading pressure within the chamber 31 the switch 14 or 15, as the case may be, will be opened, deenergizing the solenoid I00. To prevent the quick return of the stem 55 to the normal position before the correct ratio of vapor flow to rate of air flow is reestablished I show connected to the plunger IOI a dashpot generally indicated at I02. The dashpot I02 serves to retard the return of the stem 55 to the normal position, thereby permitting the fan speed change and positioning of the damper to counteract such change to be consummated before the retarding action effected by the valve 54 is again made effective.

In Fig. 5 I show a modified form of my invention adapted to a system wherein regulation of the rate of flow of the products of combustion through theuptake 5 is secured by varying the output shaft speed of a hydraulic coupling I03 driven by the variable speed motor I. As known. the output shaft speed of a hydraulic coupling may be varied as desired by altering the quantity of hydraulic fluid within the coupling. Thus increases in the volume of hydraulic fluid within the coupling eflect proportionate increases in the output shaft speed, and when the internal passages are completely filled the output shaft speed will be slightly less than the input shaft speed. Conversely, decreases in the volume of hydraulic fluid effect proportionate reductions in output shaft speed and when the coupling is empty of fluid the output shaft speed will usually be in the nature of 20% of the input shaft speed, the exact percent depending upon coupling design.

To further increase the range in fan speed available, the coupling may be driven as shown by a variable speed motor. To prevent sudden increases or decreases in fan speed when a change is made in motor speed it is desirable to immediately vary the quantity of the hydraulic fluid in the coupling to counteract changes in fan speed caused by changes in motor speed. Such changes in the quantity of hydraulic fluid within the coupling are preferably accomplished in synchronism with the acceleration or deceleration of the motor, so that during the period of transition the fan speed remains substantially constant.

To provide for varying the quantity of oil within the hydraulic coupling I03 in accordance with vapor pressure changes and deviations in the ratio between rate of vapor outflow and rate of air flow, I may employ apparatus forming a part of the subject matter of an application of Harry E. Weaver, Serial No. 27,425, filed in the United States Patent Office, June 19, 1935 now Patent No. 2,116,922. In accordance therewith a substantially constant circulation of hydraulic fluid is maintained through a'circuit comprising a portion of a pump suction pipe I04, continuously running pump I05, and a bypass line I06. Similarly a constant circulation of hydraulic fluid is maintained through a circuit comprising a diaphragm valve I01, pipe I08, diaphragm valve I09, and a portion of the pump suction pipe I04. The pressure differential across the valves I01 and I09 may be held constant by suitable regulating valves H0 and III. So long as the speed of the fan 6 is at the desired value, the flow through the diaphragm valve I01 to the pipe I08 is equal to the flow from the pipe I08 through the diaphragm valve I09 to the suction pipe I04. When, however, it is desired to increase the speed of the fan 9 for example, the diaphragm valve I01 is positioned in an opening direction, whereas the diaphragm valve I09 is simultaneously positioned in a closing direction thereby increasing the flow of hydraulic fluid to the pipe I08 above that therefrom. The difference is transmitted through a pipe II2 to the coupling inlet tube 3. Such increase in quantity of oil within the coupling I03 is effective for increasing the speed of the fan 6. Conversely, when it is desired to decrease the speed of the fan 6 the diaphragm valve I01 is positioned in a closing direction whereas the valve I09 is positioned in an opening direction, thereby increasing the flow of oil from the pipe I08 above that thereto, serving to withdraw oil from the hydraulic coupling I03. A reservoir H4 is provided wherein excess oil over that required may be stored. The hydraulic fluid within the coupling I03 may be maintained at a desired temperature by providing a constant circulation from a suitable outlet IIS and heat exchanger Hi to the inlet H3.

The diaphragm valves I01 and I09 are shown adapted to be positioned by the control pressure established within the pipe 21 in accordance with variations in vapor pressure and deviations in the ratio between rate of vapor outlflow and rate of air supply from the desired value. In order that a given change in loading pressure within the chamber 35 or chamber 53 of the averaging relay will produce a definite change in speed of the fan 5 without overtravel or hunting; the control pressure within the pipe 21 may be made proportional to the difference between the desired and actual speed of the fan Ii through the agency of the averaging relay 36. This may be accomplished by producing. through a suitable arcane! speed responsive device, a loading pressure in a chamber N1 of the averaging relay 33 proportional to the speed of the fan 0. Accordingly, the difierence between the pressures within the chamber III and chambers 35 and 53 will be efiective against the pressure established in the control chamber 31, so that the pressure transmitted through the pipe 21 to the diaphragm valves I01 and I09 will be proportional to the difference between desired and actual speed. As the latter approaches the former the diaphragm valves I01 and I09 are gradually brought to the neutral position when the flow through the valve I01 into the pipe I08 is equal to the flow therefrom through the valve I09.

A fluid pressure proportional to the speed of the fan 6 may be produced by a device forming the subject matter of an application of Paul S. Dickey entitled Measuring and control systems", filed in the United states Patent Oflice on June 19, 1935, Serial No. 27,426 now Patent No. 2,141.- 082. In accordance therewith a fluid compressor H8 is driven through suitable belt means M9 from the shaft of the fan 6. Connected in a I discharge line I20, running to the chamber III,

is a chamber I2I provided with a fixed orifice I22 of such size that the pressure of the atmosphere is below the critical pressure for the pressure within the discharge line I20. Inasmuch as the volume of fluid compressed varies directly with the speed of the compressor H it follows from Napiers Law that the pressure in the discharge line I20 will likewise be proportional to speed. Accordingly pressures within the chamber I I1 will be proportional to the speed of the fan 6.,

Under normal operation with the speed of the motor 1 remaining constant, variations in vapor pressure or a deviation in the ratio between rate of vapor outflow and rate of air supply from that desired will effect positioning of the diaphragm valves I01 and I09 to vary the quantity of hydraulic fluid in the coupling I03 to produce a change in speed of the fan 6 in desired sense and amount. When the speed of the fan 6 has reached a minimum or maximum value for the then existing speed of the motor 1, I provide means for automatically changing the speed of the motor I and simultaneously varying the quantity of hydraulic fluid in the coupling so that the speed of the fan 6 remains substantially constant throughout the period of transition. To this end I show connected to the pipe I20 a Bourdon tube I23 adapted toactuate the switches 51 and 63 at predetermined maximum and minimum pressures respectively. When the hydraulic coupling I03 is completely fllled'a definite speed of the fan 6 will be obtained, which will produce a predetermined loading pressure within the pipe I20, The Bourdon tube I23 may be adjusted so that when this pressure obtains the switch 51 is closed. Similarly when the hydraulic coupling I03 is substantially empty of fluid, resulting in a definite minimum speed of the fan 6 the Bourdon tube I23 may be adjusted to open the switch 63. increase in speed of the motor 1 through the solenoid 58 and simultaneously serves to energize the solenoid 66, whereby the plunger 01 is positioned downwardly decreasing the loading pressure effective Within the chamber 35 and resulting in the diaphragm valves- I01 and I09 being positioned in a direction to withdraw fluid from the coupling I 03; thereby tending to reduce the speed of the fan'G. Conversely, open- Closure of the switch 51 effects an ing of the switch 63 serves to reduce the speed of the motor 1 and simultaneously to effect an upward positioning of the plunger 61, thereby producing an increase in speed of the fan 6 equal to the decrease effective through the reduction in speed'of the motor 1.

In Fig. 6 I show a modifiedform of my invention wherein control of the rate of products of combustion is effected through the damper II and fan 6 operated by the hydraulic coupling I03, which is driven by a constant speed source of power such as a motor I24. Changes in the quantity of hydraulic fluid within the coupling to efi'ect desired speed changes of the fan 6 are obtained through actuation of the pump I in proper direction to introduce fluid from the reservoir I II to the inlet pipe II3, or to withdraw oil from the inlet H3 and return it to the reservoir IM. Operation of the pump I05 in proper direction is obtained through a reversible motor I 25 controlled through the normally open switches and 15. The motor I may be provided with suitable running switches so upon energization it will continue to run until the quantity of oil in the hydraulic coupling is changed a predetermined amount.

The damper II is po itioned through changes in control pressure establishedby the relay and upon being positioned to a substantially open position efi'ects closure of the switch 10, which energizes the motor I25 in proper direction to introduce hydraulic fluid into the coupling I03. Simultaneously closure of the switch It efiects energization of the solenoid III, which serves as hereinbefore described to modify the loading pressure established in the chamber in proper sense to position the damper II in a closing direction a suflicient amount to counteract the change in rate of flow of the. products of combustion effected through the increase in speed of the fan 6. Upon repositioning of the damper II the switch 10 is opened, deenergizing the solenoid 9i. Gradually the beam 33 is then restored to the neutral position under the influence of springs 90 and 95 and dashpot 96.

Upon a closure of the damper I I to a predetermined minimum position the switch 15 is closed, effecting energization of the motor I25 in proper direction to withdraw fluid from the hydraulic coupling I03 and simultaneously energize the solenoid 92, thereby effecting a modification of the loading pressure within the chamber 35 in proper sense to eflect a positioning of the damper II' in an opening direction a sufilcient amount to counteract the change in rate of flow of the products of combustion effected by the decrease in speed of the fan 6. Thereafter upon the mercury switch 15 being-opened, the solenoid 92 is cleanergized, permitting the beam 33 to be gradually re- I stored to the neutral or normal position.

In the modifications of my invention I have chosen to illustrate and describe, I may in place of utilizing a direct indication of the damper II to energize or deenergize the control circuit employ a more or less indirect indication. For example, referring to Fig. 7 I have shown connected to the pipe 21 pressure sensitive switches I26 and I21. The pressure switch I26 is adapted to close when the pressure within the pipe 21 reaches a predetermined maximum value, and pressure switch I21 is adapted to open when the pressure reaches a predetermined minimum value. It is apparent that the pressure within the pipe 21 is an indication of the damper position I I inasmuch as for every value of the pressure there is a deflnite damper position. Accordingly the switch I26 may be substituted for the switch 51 and the switch I21 substituted for switch 63.

In Fig. 8 I have shown normally open pressure switches I28 and I29 sensitive to the pressure within the conduit 21. It is apparent that the switch I28 may be substituted for the switch 14; and the switch I29 for the switch 15.

The term "control couple as used in the appended claims refers to a device such as a pilot valve illustrated at I3 or I3b. This device has a valve stem and a valve body relatively movable and it is through the relative movement of these two elements that a fluid pressure proportional to the controlled condition is obtained. The term control couple is not limited to a pilot valve however, but the term is intended to include substantially any sensitive device which is used to establish or produce a control force, whether that control force be a fluid pressure, an electromotive force, or periodic electric impulses of a time length proportional to the magnitude of the controlled condition.

While in the foregoing description I have described certain forms of my invention, it is apparent that it may be embodied in further forms and modifications; that it is not limited to the control solely of vapor generators but may be applied to any apparatus wherein an agent or agents contributing to the production or maintenance of a condition are supplied through supply means having a plurality of rates of operation.

What I claim as new, and desire to secure by Letters Patent of the United States, is:

1. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, a regulator for an agent affecting said condition positioned by said fluid pressure, and electromagnetic means under the control of said regulator and mechanically connected to one of said elements for relatively moving said elements at a predetermined position of said regulator.

2. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, means for supplying an agent afiecting the condition having a plurality of rates of operation, a regulator positioned by said fluid pressure for modifying the rate of supply of said agent in accordance with variations in the magnitude of the controlled condition, and means actuated at predetermined positions of said re ulator to vary the rate of operation of said supply means and means actuated by said regulator independently of the change in rate of operation of said supply means to simultaneously vary said fluid pressure to position said regulator to effect a substantially equal change in the rate of supply of said agent as effected by the change in rate of operation of said supply means but in opposite sense.

3. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for relatively moving said elements in response to changes in the magnitude of a controlled condition, means for supplying an agent aflecting the condition having a plurality of rates of operation, a regulator positioned by said fluid pressure for modifying the rate of supply of said agent in accordance with variations in the magnitude of the controlled condition, means for changing the rate of operation of said supply means at a predetermined position of said regulator and means actuated independently of the change in rate of operation of said supply means for simultaneously modifying the fluid pressure to effect a change in position of said regulator to substantially counteract the change in rate of agent supply efiected by said change in rate of operation; and means operated at a different predetermined position of said regulator for reverting said supply means to the original rate of operation and means actuated independently of the change in rate of operation of said supply means for simultaneously modifying the fluid pressure to effect a change in position of said regulator to substantially counteract the change in rate of agent supply effected by said change in rate of operation.

4. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, means for supplying an agent affecting the condition having a plurality of rates of operation, a regulator positioned by said fluid pressure for modifyingthe rate of supply of said agent in accordance with variations in the magnitude of the controlled condition, means actuated at predetermined positions of said regulator to vary the rate of operation of said supply means, means for simultaneously moving one of said elements to vary said fluid pressure to counteract the change in rate of supply of said agent caused by said change in rate of operation of said supply means; and retarded means for annuling said last named change in fluid pressure.

5. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, means for supplying an agent affecting the condition having a plurality of rates of operation, means for producing a second fluid pressure in accordance with the rate of supply of said agent, a relay for producing a third fluid pressure in accordance with a function of the sum of said first two fluid pressures, means for retarding the effect of said second fluid pressure in said relay, a regulator for said agent positioned by said third fluid pressure, means actuated at predetermined positions of said regulator to vary the rate of operation of said supply means; and means for simultaneously rendering said retarding means non-effective.

6. In combination, a duct, a multi-speed fan for producing a flow of fluid in said .duct, a

damper in said duct, a servo-motor for positioning said damper, and means under the control of said servo-motor for changing said fan speed when said damper reaches predetermined positions and simultaneously operating said servomotor to position said damper to efiect a change in fiow of fluid through said duct in opposite direction to that caused by the change in fan speed.

7. In combination, a duct, a multi-speed fan for producing a flow of fluid in said duct, a damper in said duct, a'fluid pressure actuated servo-motor for positioning said damper, means under the control of said servo-motor for changing fan speed when said damper reaches a predetermined position; and means also controlled by said servo-motor for simultaneously changing the fluid pressure effective in said servo-motor to position the damper to counteract the change in flow of fluid caused by the said change in fan speed.

8. In a combustion control system for a vapor generator, in combination, air supply means having a plurality of rates of operation, regulating means for the air supply, means for producing a first fluid pressure in proportion to the pressure of the vapor generated, a servo-motor sensitive to said fluid pressure for positioning said regulating means, and means actuated by said regulating means independently of said change in rate of operation of said air supply means, for changing the magnitude of the fluid pressure for a given magnitude of vapor pressure predetermined amounts upon changes in the rate of operation of said air supply means.

9. In a combusticm control system for a vapor generator, in combination, fuel and air supply means, means for producing a fluid pressure in accordance with vapor pressure, a regulator for the air supply under the control of said fluid pressure, means under the control of said regulator for varying the rate of operation of said air supplying means, and means simultaneously operated by said regulator independently of the change in speed of air supplying means for varying the fluid pressure to effect a change in the rate of air supply in opposite direction to that caused by the change in the rate of operation of the air supply means.

10. In a combustion control system for a vapor generator, in combination, a fan for supplying air to the generator, a multi-speed motor for operating said fan, a damper for regulating the rate of air supply, a servo-motor for operating said damper, means for establishing a fluid pressure in accordance with a condition affected by the rate of air supply for controlling said servo-- motor, and means operated by said servo-motor at predetermined positions for varying the speed of said motor and simultaneously independently of said change in fan speed modifying said fluid pressure to effect a change in position of said damper.

11. In a combustion control system for a vapor generator, in combination, air supply means having a plurality of rates of operation, regulating means for the air supply, means for producing a first fluid pressure in accordance with the vapor pressure, means for producing a second fluid pressure in accordance with the ratio between rate of vapor outflow and rate of air supply, a relay for producing a third fluid pressure in accordance with the magnitude of the first and second fluid pressures, a servo-motor actuated by the third fluid pressure for positioning said regulating means, means for retarding the admission of said second fluid pressure to said relay, and means for rendering said retarding means ineffective for an increment 'of time upon a change in the rate of operation of said air supply means.

12. In combination, a hydraulic coupling having an output shaft, a duct, a fan connected to said duct and driven by said output shaft, a damper in said duct, a servo-motor for positioning said damper, means for producing a fluid pressure effective for actuating saidservo-motor, means actuated by said servo-motor at predetermined. positions of said damper for varying the hydraulic fluid in said coupling to effect a change in fan speed and simultaneously change said fluid pressure to effect a positioning of said damper to counteract the said change in fan speed; and retarded means for subsequently annuling said change in fluid pressure.

13. In combination, a hydraulic coupling having an output shaft, a multi-speed motor for driving said coupling, a tachometer for producing a first fluid pressure in accordance with the output shaft speed, means for producing a second fluid pressure, a relay for producing a third fluid pressure bearing a functional relation to the al-- gebraic sum of the first and second fluid pressures, means actuated by said third fluid pressure controlling the admission and discharge of hydraulic fluid to the coupling, and means sensitive to a predetermined value of the first fluid pressure for changing said motor speed and simultaneously modifying the second fluid pressure to effect a change in speed of said output shaft in opposite sense to that caused by the change in motor speed.

14. In combination, a hydraulic coupling having an output shaft, a multi-speed motor for driving said coupling, means for producing a fluid pressure, means actuated by said fluid pressure controlling the admission and discharge'of hydraulic fluid to and-from the coupling, and means sensitive to a predetermined value of the fluid pressure for changing said motor speed and simultaneously independently of the change in output shaft speed caused by the change in motor speed varying the hydraulic fluid in said coupling to vary the speed of the output shaft in opposite sense to that caused by the change in motor speed.

15. In combination, a hydraulic coupling having an output shaft, a fluid impeller driven by said output shaft, means for producing a fluid pressure, a regulator of the fluid passing through said impeller positioned in accordance with said fluid pressure; and means actuated by said regulator at predetermined positions for varying the hydraulic fluid in said coupling and simultaneously varying said fluid pressure to position said regulator to effect a change in fluid flow in opposite sense to that caused by said variation in hydraulic fluid.

16. In combination, a hydraulic coupling having an output shaft, a duct, a fan connected to said duct and driven by said output shaft, a damper in said duct, a servo-motor for positioning said damper, means for' producing a fluid pressure effective for actuating said servo-motor, and means actuated by said servo-motor at predetermined positions of said damper for varying the hydraulic fluid in said coupling to effect a change in fan speed.

17. In a control system for fluid flow, a hydraulic coupling having ail-output shaft, a fluid impeller driven by said output shaft for effecting said fluid flow, valve means interposed in the path of said fluid flow, and means for varying the quantity of fluid in said coupling by and in accordance with the position of said valve means.

18. In combination, a hydraulic coupling having an output shaft, a duct, a fan connected to said duct and driven' by said output shaft, a, damper in said duct, a servo-motor for positioning said damper, means for producing a control force effective for actuating said servo-motor, means actuated by said servo-motor at predetermined positions of said damper for varying the hydraulic fluid in said coupling to effect a change in fan speed and simultaneously independently of the change in fan speed change said control force to eifect a positioning of said damper to counteract; the said change in fan speed.

19. In combination, a hydraulic coupling having an output shaft, a duct, a fan connected to said duct and driven by said output shaft, a damper in said duct, a servo-motor for positioning said damper, means for producing :a control force eiiecbive for actuating said servo-motor, means actuated by said servo-motor at predetermined positions of said damper for varying the hydraulic fluid in said coupling to efiect a change in fan speed and simultaneously change said control force to effect a positioning of said damper to counteract the said change in fan speed, and retarded means for subsequently annulling said last change in control force.

' 20. In combination, a hydraulic coupling having an output shaft, a multi-speed motor for driving said coupling, means for producing a control force, means actuated by said control force controlling the admission and discharge of hydraulic fluid to and from the coupling, and means sensitive to a predetermined value of the control force for changing said motor speed and simultaneously independently of the change in output shaft speed caused by the change in motor speed varying the hydraulic fluid in said coupling to vary the speed of the output shaft in opposite sense to that caused by the change in motor speed.

21. A control system, comprising a control couple having relatively movable elements for governing the control force in the system, means for positioning one of said elements respons've to the magnitude of a controlled condition, a regulator for an agent affecting said condition pos'tioned by said control force, and means directly actuated by said regulator for relatively moving said element a predetermined amount at a predetermined position of said regulator.

22. A control system comprising a control couple having relatively movable elements for governing the control force in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, means for supplying an agent affecting the condition having a plurality of rates of operation, a regulator positioned by said control force for modiiying the rate of supply of said agent in accordance with variations in the magnitude of the controlled condition, and means actuated at predetermined positions of said regulator to vary the rate of operation of said supply means and simultaneously independently of the change in rate of operation of said supply means to position said regulator to efiect a substantially equal change in the rate of supply of said agent as afiected by the change in the rate of operation of said supply means but in opposite sense.

23. A fluid pressure control system comprising a control couple having relatively movable elements for governing the fluid pressure in the system, means for positioning one of said elements responsive to the magnitude of a controlled condition, a regulator for an agent affecting said condition positioned by said fluid pressuraan electric circuit, electro-magnetic means in said circuit for positioning one of said elements, and control means for said circuit actuated by said regulator at a predetermined position thereof.

'24. In a combustion control system for a vapor generator, in combination, fuel and air supply means, means for producing a fluid pressure in accordance with the pressure of the vapor generated, regulating means of the fuel supply under the control of said fluid pressure, and means responsive to failure of the air supply means for changing said fluid pressure to cause said regulator to move to a predetermined position.

25. In a combustion control system for a vapor generator, in combination, fuel and air. supply means, means for regulating the rate of fuel and air supply, and means responsive to an abnormal condition of said air supply means for causing said regulating means to move to a predetermined position.

26. In a combustion control system for a vapor generator, in combination, fuel and air supply means for the generator, means for producing a first fluid pressure, regulating means of the fuel supply under the control of said first fluid pressure, means for producing a second fluid pressure, regulating means of the air supply under the control of said second fluid pressure, and means for changing both said first and second, fluid pressures a predetermined amount to cause said fuel and air regulating means to move to a closed position upon failure of said air supply means.

WALTER E. DUERINGER. 

